Releasable tool for clicker die press



July 24, 1962 B. c. EISENBERG 3,045,521

RELEASABLE TOOL FOR CLICKER DIE PRESS Filed July 9,' 1958 4 Sheets-Sheet 1 0 N {o k N) l 55; 1 \1 4 I A. L 1

INVENTOR. BERNARD C.EISENBERG BY &4;, &, W

ATTORNEY July 24, 1962 B. c. EISENBERG 3,045,521

RELEASABLE TOOL FOR CLICKER DIE PRESS Filed July 9, 1958 4 Sheets-Sheet 2 FIG.7

INVENTOR. BERNARD C. EISENBERG ATTOR N EY B. C. EISENBERG RELEASABLE TOOL FOR CLICKER DIE PRESS July 24; 1962 4 Sheets-Sheet 3 Filed July 9, 1958 INVENTOR. BERNARD C.EISENBERG f if M? x w W e Y B 4 v 3 2: MW 4 5 F 4 A a 3 w\\\\ -x$ :9 w 7 VIII/ 7;!!! 00 4 W we 4 7 J l 4 9 3 4 3 L f 7 3 MW ATTOR NEY Jul 24, 1962 B. c. EISENBERG RELEASABLE TOOL FOR CLICKER DIE PRESS glfietg-gsheet 4 Filed July 9, 1958 FIGS FIG.4

JNVENTOR.

BERNARD C.EISENBERG BY 6%? 4% ATTORN E Y Filed July 9, 1958, Ser. No. 747,529 12 Claims. (Cl. 83-532) This invention relates to machines for cutting sheet material, and more specifically, concerns machines for cutting such material by a cutting die; the die being in contact with the material and adapted to be struck by impact to effect the cutting action.

It has been proposed to cut sheet materials such as fabric, felt, leather, rubber, plastic and the like, in single or multiple layers; by cutting dies having the outline of the shape to be cut from the sheet material. The die is driven through one or more superposed layers of material by applied pressure, as by means of a hammer, pressure plate or the like.

However, known devices of the character described are cumbersome in operation, bulky and complicated as to structure. Furthermore, such devices have a rather slow cycle of operation and thus show a relatively low production rate in use.

Accordingly, an object of this invention is to provide an improved die cutting machine having a minimum number of parts; which has a high speed operational cycle; is readily and quickly manipulated in use; and incorporates an improved safety system which precludes injury to the operator.

Another object of this invention is to provide a machine of the character described, which includes a pneumatically driven hammer for maximum impact with respect to the cutting die together with improved means for repositioning the hammer for its subsequent operative movement.

A further object of this invention is to provide in a machine of the character described, means for counterbalancing a hammer assembly to facilitate the positioning of a clicker die detachably mounted on the assembly for receiving the impact of the hammer; together with improved means for locking the position of the assembly simultaneously with the actuation of the hammer to avoid upward rebound of the assembly.

Still another object of this invention is to provide in a machine of the character described, electrical control means for regulating the operation of the means for actuating the hammer and other control means for adjusting the degree of impact produced by the falling hammer to suit the nature of the work.

Other objects of this invention will in part be obvious and in part hereinafter pointed out.

In the drawing, FIG. 1 is a side elevational view of a machine embodying the invention; FIG. 2 is a top plan view thereof; FIG. 3 is a vertical sectional view of the hammer assembly portion of the machine; FIG. 4 is a side elevational view of the assembly showing the braking and counterbalance components thereof; FIG. 5 is a top plan view thereof; FIG. 6 is a front elevational view of a handle portion of the device, with parts in section; and FIG. 7 is an end view thereof.

Referring in detail to the drawing, and particularly to FdGS. l and 2 thereof, 10 designates a device embodying the invention. The same comprises a cutting block 11 adapted to support on its cutting surface 12, sheet ma terial not shown, which may be in single or multilayer form, and is to be cut into elements of predetermined outline.

A post 13 in vertical position, is located adjacent one end of block 11 and extends upwardly well above cutting surface 12. A horizontally extending bracket 14 made up of a pair of opposed plates welded at their inner ends States atent of post 13 by means of said sleeve.

to a sleeve 15, is swivelly mounted on the upper portion A pair of spaced collars fixed to post 13, locate bracket 14 in proper position above block 11.

A second bracket 17 made up also of a pair of opposed plates, is swivelly mounted at its inner end, to the outer end of bracket 14. To this end, the outer ends of bracket plates 14 are welded to a vertical tubular member 18, and similarly, the inner ends of bracket plates 17 are welded to a vertical tubular member 19. Horizontal hinge plates 20 are welded at one end thereof to the opposite ends of tubular member 18 and a shaft 21 coaxiallydisposed within tubular member 19 and fixed thereto, has its opposite ends journalled in the other end of hinge plates 20. Collars 22 on the opposite ends of shaft 21 complete the swivel connection between brackets 14, 17, allowing said brackets to be manipulated in a manner to locate the outer end portion of bracket 17 in any desired position over the cutting surface 12 of block '11.

A verticallly positioned hammer assembly generally indicated at 23 is mounted on bracket plates 17. To this end, a pair of opposed mounting plates 24 are bolted to the outer ends of bracket plates 17, said plates 24 being held in spaced relation by a cross member 25. At the forward ends of mounting plates 24, a pair of similar, aligned, circular looped members 26 are welded in place to slidably receive therein a cylindrical member 27 of assembly 23.

. Fixed between mounting plates 24, is a conventional spring type counterbalance generally indicated at 28, as shown in FIG. 4, the usual metal tape 29 of balance 28 extending downwardly between plates 24 and secured to a surface portion of cylindrical member 27 by a shackle 3! The capacity of counterbalance 28 is selected in terms of the total weight of assembly 2-3 so as to allow easy vertical adjustment of said assembly with respect to cutting surface 12.

As shown in FIG. 3, cylindrical member 27 is closed at its upper end by a threaded-plug 31 having a central threaded opening 32 for receiving the threaded end of a conduit 33, for the purpose hereinafter described. The lower end of cylindrical member 27 is also threaded internally to receive an externally threaded member 34 having a bore 35 and a radial passage 36 communicating with bore 35. Handle means 37, 38 extend laterally from the lower portion 39 of member 34 to readily turn member 34 with respect to cylindrical member 27.

A cutting or clicker die 40 of predetermined cutting outline is adapted to be detachably mounted on member 34, said die having a shank 41 receivable in bore 35. Shank 41 is formed with a radial recess 42 adapted to register with the inner end of passage 36 of turnable member 34, for the purpose hereinafter appearing.

Within cylindrical member 27 is disposed a hammer '43 freely slidable Within said member and adapted to deliver a sharp impacting blow to die shank 41, upon accelerated downward movement from the top portion of member 27.

Means is provided for accelerating the downward movement of hammer 43, as well as restoring said hammer to its elevated position, after the die shank 41 has received the impacting blow. To this end, conduit 33 at the upper end of cylindrical member 27 is connected by a T connection 44 of flexible conduit to a source of compressed Switch means is provided to control the operation of solenoids 48, 50, whereby valve 49 may be closed and valve 47 opened to admit air under pressure from source 45 to cylindrical member 27. To this end, a manually operated switch 51 is mounted in handle means 37, while a manually operated switch 52 series connected with switch 51, is mounted in handle means 38. As shown in FIG. 3, an adjustable timing relay 53 is connected in circuit with switches 51, 52 and solenoids 48, 50.

It will be apparent that upon operation of both switches 51, 52, thereby insuring that the operators hands are on handle means 37, 38 and out of the way of cutting die 40; timing relay 53 is energized from line L to close the circuit to solenoids 48, St) to energize the same and thereby open valve 47 and close valve 49. The hammer 43, free of the influence of vacuum from source 46, will drop with accelerated movement due to the admission of compressed air to cylindrical member 27 from source 45, to deliver a sharp blow to die shank 41 and thus cut whatever material is on cutting surface 12 of block 11 by means of die 40.

The degree of impact of hammer 43 on shank 41 may be regulated by adjusting the timing relay 53 to open the circuit to solenoids 48, 50 at the end of selected time intervals, thereby regulating the time interval during which valve 47 is open. Furthermore, a pressure regulator 54 between source 45 and valve 47 can adjust the pressure of the air coming into cylindrical member 27, and thereby further regulate the extent of the impact of hammer 43, in accordance with the nature and thickness of the material to be cut by die 40.

Means is also provided for detachably mounting die 40 on turnable member 34, as shown in FIG. 6. Thus, handle means 38 comprises an upwardly curved member 55 having a laterally extending, inverted channeled member 56 fixed to the upper end thereof. An inverted channeled member 57 is telescoped with respect to member 56 and pivoted thereto at the inner end thereof as at 58. A coiled spring 59 mounted between members 56, 57 at the outer ends thereof, biases said members away from each other.

Pivoted member 57 includes at its inner end, downwardly extending ear portions 60 which are loosely connected through slots therein, to a vertically disposed, channel shaped link 61, by means of a cross pin 62. The flange portions 61a of link 61 are pivoted on cars 62 extending from an intermediate portion of member 55, by

' a cross pin 64.

The Web portion of link 61 is formed at its lower end with an open end slot 65. A lock pin 66 is slidably mounted in passage 36 of member 34; said pin being connected to link 61 by having its outer end passing through link slot 65. Spaced collars 67, 68 on the outer end of pin 66 allows for a loose connection between pin 66 and link 61.

Normally, member 57 will be pivoted to a raised position relative to member 56, by action of spring 59, thereby moving lock pin 66 inwardly to locate the end thereof in recess 42 of die shank 41, thus holding die 40 in associated relation to member 34 and allowing hammer assembly 23 to be moved in vertical directions and to locate the die over cutting surface 12.

When die 40 is properly located and is placed in resting contact with the material to be cut, switch 51 is closed by one hand of the operator, while switch 52, which is located between handle members 56, 57, is operated when member 57 is pressed downwardly to the position shown in FIG. 6, thereby causing hammer 23 to drop with accelerated movement, as described above.

The actuation of switch 52 by reason of downward pivoted movement of handle member 57, also causes lock pin 66 to be Withdrawn from recess 42 in die shank 41. Thus, shank 41 is free to receive the impact of hammer 43; allowing shank 41 to move downwardly with respect to member 34 in the cutting movement of die 40. On release of handle member 57, pin 66 reengages die shank 41 to allow assembly 23 to be lifted so as to relocate die 40 for its next cutting operation.

Since the hammer 43 descends with great speed and is of a substantial weight, theremay be a tendency for assembly 23 to rebound somewhat in an upward direction thereby impairing the full impact effect of the hammer with respect to the material to be cut. Accordingly, provision is made to lock the position of assembly 23 with respect to mounting plates 24 and brackets 14, 17. For this purpose, a small air cylinder 69 is mounted in an opening in one of the plates 24 to locate its piston actuated stem 70 in transverse relation to said plates and extending toward the other plate 24.

A brake shoe plate 71 is loosely mounted on stem 70 and carries a layer of friction material 72. Said plate 71 is adapted to press layer 72 tightly against opposed portions of a fiat, vertically disposed member 73 which is fixed at its opposite ends by lateral extensions thereof to surface portions of cylindrical member 27. A supplemental layer of friction material 74 may be fixed to the inner surface portion of the other plate 24 in opposed relation to layer 72.

Air cylinder 69 is connected by a conduit 75 to a branch of T connection 44, at a point adjacent conduit 33 on cylinder 27. Thus, when valve 47 is opened to admit compressed air to cylinder 27, after the die carried by the cylinder has been properly located over cutting surface 12, air is also supplied to cylinder 69. Stem 70 will then be projected to move brake shoe 71 into gripping relation with the opposed portion of member 73, backed up by friction material 74. Accordingly, cylinder 27 will be locked in its adjusted position relative to cutting block surface 12 and when hammer 43 delivers its blow to die shank 41, there will be no rebound of said cylinder away from said cutting surface.

When valve 47 is closed and valve 49 is opened, the resultant vacuum which restores hammer 43 to its elevated position, also acts on cylinder 69 to retract brake shoe 71 and thus release cylinder 27 for free vertical movement. In addition, brake shoe 71 may be spring biased to its normally retracted position.

An air release valve 76 may be located on a Wall portion of cylinder 27, said valve being biased by a spring 77 against a seat 78 in wall opening 79. The cumulative eifect of the air under pressure admitted to cylinder 27 for driving hammer 43 downwardly, is dissipated as the pressure rearwardly of said hammer reaches a point at Which the biasing action of spring 77 is overcome. Openings 80 in the wall of cylinder 27 at the lower end thereof, allow the air ahead of the downwardly moving hammer 43 to escape from said cylinder.

While die 40 is shown as integral with shank 41, it is understood that various dies in conventional form may be detachably mounted on a collar portion of a shank provided with suitable means for holding such dies on said collar portion.

'The arrangement of brackets 14, 17, as shown, permits bracket 17 to be folded back against bracket 14, when not in use, as well as extreme flexibility for positioning assembly 23 anywhere over the cutting block surface 12. Cylinder 27 may be readily moved up or down to adjusted positions, through the action of counterbalance 28. With the arrangement shown, cutting dies alone or integrated with a die shank, may be quickly interchanged, by manipulation of handle member 57 or the attaching means on the die shank collar.

The timing of relay 53 may be adjusted, with or without adjustment of pressure regulator 54, to insure efficient cutting action of die 40 in response to the impact of hammer 43, thus taking into account sheet materials of varied nature and any thickness thereof.

As various changes might be made in the embodiment of the invention herein described, Without departing from the spirit thereof, all matter herein shown or described shall be deemed illustrative and not by way of limitation except as set forth in the appended claims.

Having thus described my invention, I claim as new and desire to protect by Letters Patent:

1. A sheet material cutting machine comprising horizontally disposed fixed cutting surface means, a vertically positioned cylinder, means for mounting said cylinder for regulated movement towards and away from said cutting surface means, a cutting die having an upwardly extending shank portion, means for releasably mounting said die shank portion in the lower end of said cylinder, hammer means freely movable Within said cylinder for free gravitational downward movement from an elevated position thereof to freely strike said die shank portion, pressure differential means connected to said cylinder selectively operable to accelerate the downward movement of said hammer means and to raise said hammer means to its elevated position within said cylinder, and means for releasing said die shankportion from the lower end of said cylinder upon downward movement of said hammer means to allow independent movement of said die when struck by said hammer means.

2. A machine as in claim 1 and further including means for regulating said pressure differential means to vary the striking etfect of said hammer.

3. A cutting machine comprising cylinder support means, horizontally disposed fixed cutting support means, a vertically disposed cylinder slidably mounted on said cylinder support means for free movement toward and away from said cutting means, a cutting die having a shank portion movably mounted at the lower end of said cylinder, a hammer within said cylinder movable downwardly by gravitation from an elevated position to deliver an impacting blow to said die shank, means on said cylinder support and operatively connected to said cylinder to counterbalance said cylinder for ready vertical movement of said cylinder relative to said cutting support means, means for accelerating the gravitational movement of said hammer, and means operative simultaneously with the operation of said accelerating means for locking the position of said cylinder relative to said cylinder support to prevent relative vertical movement between said cylinder and said support upon impact of the die shank by said hammer.

4. In a cutting machine of the character described comprising a vertically disposed cylinder, a member turnably mounted within the lower end of said cylinder about a vertical axis, said member being formed with a bore, a cutting die having a shank portion slidably received in said bore, movable means on said turnable memberengageable with said shank portion for releasably connecting said die to said turnable member, a hammer arranged for gravitational movement in said cylinder to strike said die shank, and means operative upon the downward movement of said hammer for actuating said movable means to disengage said shank from said turnable member whereby said die shank portion is freely movable within the bore of said turnable member when said die shank portion is struck by said hammer.

5. In a cutting machine of the character described, a cylinder support, a vertically disposed cylinder mounted on said support, a closure turnably mounted in the lower end of said cylinder, said closure being formed with an axial bore, a cutting die having a shank portion slidably received in said bore, movable lock means on said closure for releasably engaging said die shank to restrain said shank against axial mo vement relative to said closure, a hammer slidably mounted in said cylinder for engagement with said die shank upon downward movement thereof, releasable means for retaining said hammer in an elevated position within said cylinder, handle means on said turnable closure, and control means on said handle means for simultaneously operating said release means to release said hammer and for actuating said lock means to the disengaged position thereof.

6. In a cutting machine as in claim 5 wherein said shank is formed with a radial recess, said lock means comprises a lock pin slidably mounted on said closure means, the inner end of said lock pin being receivable in said recess, said actuating means comprising a pivoted handle portion and link means connecting said handle portion and the outer end of said lock pin.

7. A cutting machine comprising a cylinder support, a vertically disposed cylinder slidably mounted on said support, balance means for holding said cylinder in selected vertical positions, a cutting die having a shank portion releasably mounted at the lower end of said cylinder, a hammer within said cylinder movable downwardly from an elevated position within said cylinder to deliver a blow to said shank portion, means for releasing said die shank portion from said cylinder end upon downward movement of said hammer, brake means for locking said cylinder relative to said cylinder support upon downward movement of said hammer.

8. A cutting machine as in claim 7 and further including a source of air under presure, conduit means connecting said source andthe upper end of said cylinder, valve means in said conduit for controlling the admission of air to said cylinder, said brake means including pneumatic actuating means, and conduit means connecting said actuating means with said first mentioned conduit means whereby said brake means is actuated upon admission of air to said cylinder.

9. A cutting machine as in claim 8 and further including air relief valve means on said cylinder for bleeding the air column within said cylinder above the downwardly moving hammer.

10. A die cutitng machine comprising a vertically disposed cylinder, a cutting die having a shank portion releasably mounted in the lower end of said cylinder, a hammer in said cylinder arranged for free gravitational movement to strike said shank portion, support means for said cylinder including means for locating said cylinder in selected positions over a horizontal surface carrying material to be cut by said cutting die, means for releasing said die shank portion upon downward movement of said hammer to allow movement of said die relative to said cylinder when said die shank portion is struck by said hammer, means on said support means for mounting said cylinder for axial movement towards and away from said horizontal surface, and balance means for holding said cylinder in a selected axial position thereof 11. A die cutting machine comprising a horizontally disposed cutting surface means, a cylinder support, a vertically disposed cylinder arranged for free slidable movement on said cylinder support towards and away from said cutting surface means, a cutting die having an upwardly extending shank portion releasably mounted in the lower end of said cylinder, a hammer in said cylinder arranged for free downward gravitational movement therein to strike said die shank portion, means for releasing said die shank portion for relative movement to said cylinder end upon downward movement of said hammer, and counterbalance means on said cylinder support and operatively connected to said cylinder for 10- eating said cylinder in adjusted positions relative to said cutting surface means.

12. A machine as in claim 11 and further including brake means engageable with a portion of said cylinder and means for actuating said brake means upon operation of said die shank release means for locking said cylinder against movement relative to said cutting surface means when said die shank portion is struck by said hammer means.

References Cited in the file of this patent UNITED STATES PATENTS 7 UNITED STATES PATENTS Eden May 17, 1910 Thomas June 10, 1913 Hunter July 7, 1914 Knott May 23, 1922 Pierce Jan. 25, 1927 OGorman June 20, 1933 8 Nast June 28, 1938 OShei Mar. 28, 1944 Wales Nov. 28, 1944 Ryan June 11, 1946 Mead Dec. 26, 1950 Temple Apr. 24, 1951 Wales Apr. 22, 1952 Pfister Nov. 5, 1957 

